Counter flow-dual pressure vent section deaerating surface condenser

ABSTRACT

Various forms of surface condensers are disclosed each respectively with a dual pressure deaerating system for condensate using a true counter-flow tray stack section. The tray stack section is disposed within reheating chamber and below a vent condenser chamber through which non-condensible gases are withdrawn from the condenser. Both the reheating chamber and the vent condenser chamber are pressure-isolated by trap means from the associated condenser space. Thus, variations in condenser load are not reflected by pressure changes in the deaerating system and the efficiency of the deaerating system is maintained. Reheating steam introduced into the reheating chamber below the level of the tray stack, flows through the tray stack, counter to the direction of flow of condensate, and to the vent condenser chamber which is maintained at a relatively lower pressure by an ejector. The true counterflow of steam through the tray stack both reheats the condensate and accommodates the separation of non-condensible gases from the condensate. One or more of the tray stack trays is disclosed to be of a construction having serrations along both its upper and lower edges to establish a plurality of drop points for the condensate.

United States Patent Wyzalek et al.

[54] COUNTER FLOW-DUAL PRESSURE VENT SECTION DEAERATING SURFACE CONDENSER [72] Inventors: Leonard J. Wyzalek,

Plains; Henry W, Peterson, Millington, both of NJ.

[73] Assigneei WorthingtonCor'poration, Harrison,

NJ. 221 Filed: Dec.31, 1970.

21 Appl.No.: 103,074

[52] US. Cl .,....l65/112, 60/95 R, 165/113 [51] Int. Cl... ..F2 8b 9/10 [58] Field of Search ..l65/112, 111, 113; 60/95 R [56] References Cited UNITED STATES PATENTS 3,153,329 10/1964 Sebald ..60/95 R X 2,956,784 10/1960 Parkinson ..165/l12 3,363,678 1/1968 Forster et a1. ..165/112 1,312,512 8/1919 Baumannu" ..165/112 1,769,746 7/1930 MacNeill... ..l65/112 2,663,547 12/1953 Evans, Jr, et al. ..165/l12 3,151,461 10/1964 Sebald et a1 ..60/9 5 R X Primary Examiner-Albert W. Davis, Jr. Attorney-Popper, Bain, Bobis & Gilfillan Pompton [4 1 Oct. 17, 1972' 57 y ABSTRACT Various forms of surface condensers are disclosed each respectively with a dual pressure. deaerating system for condensate using a true counter-flow tray stack section. The tray stack section is disposed within reheating chamber and below a vent condenser chamber through which non-condensible gases are withdrawn from the condenser. Both the reheating chamber and the vent condenser chamber arepressure-isolated by trap means from the associated con- 'denser space. Thus, variations in condenser load are 1 not reflected by pressure changes in the deaerating system and the efficiency of the deaerating system is maintained. Reheating steam introduced into the reheating chamber below the level of the tray stack,

' flows through the tray stack, counter to the direction of flow of condensate, and to the vent condenser chamber which is maintained at a relatively lower pressure by an ejector. The true counterflow of steam through the tray stack both reheats the condensate and accommodates the separation of non-condensible gases from the condensate. One or more of the tray stack trays is disclosed to be of a construction having serrations along both its upper and lower edges to establish a plurality of drop points for the condensate.

9 Claims, 7 Drawing Figures PATENTED 3.698.476

SHEET 1 BF 4 LEONARD J. WYZ ALEK HENRY W. PETERSON INVENTOR.

BY W

PATENTEDucI n ma 3.698.476

SHEU 2 OF 4 FIGZ FIG. 3 LEONARD J. WYZALEK HENRY w. PETERSON INVENTOR.

PATENTED 171972 3.698.476

SHEET 3 BF 4 LEONARD J. WYZALEK HENRY W. PETERSON INVENTOR.

PATENTEDom 17 I972 3,698,47

saw u [If 4 HENRY w. PETERSON I N VENTOR.

BY wwm/gwlwvg y COUNTER FLOW-DUAL PRESSURE VENT SECTION DEAERATING SURFACE CONDENSER BACKGROUND OF THE INVENTION This invention relates generally to the field of condensers for-vapors, e.g. steam, and in particular to deaerating condensers for condensing vapors and removing non-condensible gases from the condensate, e.g., removing oxygen from steam condensate.

One of the continuing problems which has faced those concerned with the design and development of condenser equipment has been the removal of noncondensible gases from the condensate. This problem isof particular importance when the vapor being condensed is steam and the condensateis intended to be recirculated forboiler feed water because the non-condensible gases which are ordinarily found in steam condensate, 'viz. oxygen, nitrogen and rare gases, may be damaging to the metallic parts of the boilers, turbines, and other equipment being served. 7

Oxygen in particular is undesirable in boiler feel water because of the corrosion it causes on metal elements of the system. In this regard, prior art condensers often discharge condensate which contains an average of 0.03 cubic centimeter of oxygen per liter of condensate. Such an oxygen concentration is excessive for most commercial and industrial uses and, as a result, deaeration procedures have been introduced in conjunction with most condensers to enable the reduction of oxygen concentration to .01 cubic centimeter of ox ygen per liter of condensate.

Modern developments in boiler feed water systems and steam turbine operated power and industrial systems, have resulted in requirements for the removal of oxygen from condensate in such amounts as to provide a feed water oxygen concentration of 0.005 cubic centimeter per liter of condensate or better. Although deaerating condensers have become known which are capable of such deaeration, their satisfactory performance has been limited, forthe most part, to conditions of constant load in the immediate range of their design load conditions. Variations in condenser loads as well as condenser operation at relatively constant loads which are substantially removed from the condenser design loads have been found to result in failure of the deaerating condensers to satisfactorily remove the non-condensible gases, and in particular, oxygen.

SUMMARY OF THE INVENTION It is the principal object of this invention, therefore, to provide a dual pressure deaerating condenser apparatus which accomplishes satisfactory reductions in the non-condensible gaseous content of a vapor, e.g. the removal of oxygen from steam condensate without greatly increased costs either in initial investment or in operating costs.

This principal object and others not enumerated are accomplished by the apparatus of the invention, one embodiment of which may include a shell, an inlet formed in the shell for introducing a vapor to the interior of the shell, an outlet formed in the shell for permitting the withdrawal of condensate means for maintain said shell at pressures less than atmospheric pressure depending on the rate of condensation of the vapor introduced into said shell, from a hot well defined by the shell, a heat exchanger disposed within the shell for condensing the vapor to form a gas-containing condensate, means for collecting the gas-containing condensate, and deaerating for reducing the gaseous content of the gas-containing condensate including a chamber which is in communication with an apparatus for exhausting gases therefrom to maintain said chamber at apredetermined pressure less than the lowest environmental pressure occurring in said shell, a means for establishing a shower of the gas-containing condensate from the chamber to the hot well, and a means for establishing ashower of the and flow of heating vapor from the hot well to the chamber counterto the flow of the gas-containing condensate whereby the gas-containing condensate is reheated and the noncondensible gases are separated therefrom.

The present invention also contemplates the use of plural trays in establishing a shower of gas-containing condensate, at leastone tray of which can be .con-

ing the separation of non-condensible gases fromv the condensate by flashing.

BRIEF DESCRIPTION OF THE DRAWINGS A more complete understanding of the present invention may be had from the following detailed description, particularly when read in the light of the I accompanying drawings wherein:

FIG. 1 is a side elevational view of a condenser according to the invention attached to the exhaust opening of a turbine and receiving exhaust steam at a single pressure. i

. FIG. 2 is a cross-sectional, elevational view through the plane 2-2 of FIG. 1;

FIG. 3 is aview similar to FIG. 1 but showing portions of the condenser of the invention in cut-away view;

FIG. 4 is a partial, cross-sectional elevational view through the plane 4-4 of FIG. 2;

FIG. 5 is a partial cross-sectional elevational view through the plane 5-5 of FIG. 3; r

FIG. 6 is a side elevational view of an embodiment of the invention appropriate for use with steam turbines having exhausts at two different pressures and showing portions of the condenser in cut-away view;

FIG. 7 is a side elevational view depicting another DETAILED DESCRIPTION Referring therefore to FIG. 1, acondenser according to the invention, designated generally by the reference numeral 10, is shown as having its inlet opening 12 connected to the exhaust of a typical turbine 14 which is shown in phantom line.

Condenser 10 includes a shell 15 having a steam dome 16, a cooling water inlet header 17, a cooling water outlet header l8, and a main body portion which defines internally a steam space 20 (FIG. 2) and a hot well 22. Hot well 22 is provided with an outlet opening 24 through which condensate may be withdrawn from the condenser to be used, e.g. as boiler feed water.

A pair of condenser tube bundles 26a and 26b as shown in FIG. 2 extends from a tube sheet forming a wall of the inlet cooling water header 17 to a tube sheet forming a wall of the outlet colling water header 18. The tubes of these tube bundles 26a and 26b carry cooling water through the condenser in the conventional manner and define the heat exchanger means of the condenser for condensing the steam exhausting from the turbine into a gas-containing condensate.

Spaced in the medial line between the tube bundles 26a and 26b is a longitudinally extending vent condensing section 27 having tube bundles 28 therein similarly connected to the inlet header 17 and outlet header 18 so that cooling water will pass therethrough for purposes which will appear clear hereinafter.

In FIG. 2, a condensate pan generally designated 31 is shown fixedly connected within the condenser shell below the tube bundles 26a and 26b. The condensate pan includes spaced trough portions 32a and 32b respectively, with upwardly extending sidewalls as at 33a and 33b, fluid seal portions 34a and 34b also spaced from each other and a central or chamber floor portion 35.

The fluid seal portions 32a and 32b extend downwardly in a direction opposite from the upwardly extending sidewalls 33a and 33b and each have one respective sidewall as at 36a 36b connected to an adjacent end, of the trough portions 34a and 34b remote from the upwardly extending sidewall 33a and 33b and the other respective sidewall as at 36c and 36d which extend upwardly to a greater height than the spaced associated sidewalls 36a and 36b forming the fluid seal portion where they are connected at opposite sides or edges of the central or chamber flow portion 35.

The vent condenser section 27 is disposed above the central or chamber floor portion '36 and disposed about the vent condenser section 27 is a longitudinally extending hood 29 which coacts with the condensate pan 3] to form a vent condenser chamber 30 as will now be described.

Thus, by reference to FIGS. 2 and 3, the hood 29 is shown to fully enclose the vent condenser section 27 and at the lower end thereof has depending side walls 39 and 40 which extend downwardly into the respective spaced fluid trap seal portions 34a and 34b of the condensate pan 31 to define when fluid is disposed therein as hereinafter described a fluid trap path. The spaces defined by the hood 29 and the central or chamber floor portion 36 of condensate pan 31 constitutes the vent condenser chamber 30. The vent condenser chamber 30 is in fluid communication with the vent condenser section 27, and communicates with an ejector 41 connected by pipe means 41a to the'upper end of the hood 29.

The ejector 41 actsto maintain a desired vacuum pressure in the vent condenser chamber so that the pressure therein will at all times be lower than the environmental pressure in condenser shell 15 during operation. I The condenser -shell 15 itself has conventional evacuating equipment (not shown) to maintain a suitable vacuum pressure therein for accommodating the turbine the blow of steam from the exhaust. i

In the space on the side of the central or chamber floor portion 36 remote from the vent condenser chamber 30, a reheat chamber 42 is formed by and between thesidewalls 36c and 36d and the central or chamber floor portion 36 whenever the fluid in the hot well 22 rises above the lowermost point of the sidewalls 36c and 36d during the operation of the condenser 10. It is thought obvious that the structure and parts of the condensate pan 31 can be so designed and placed that the level of fluid in the hot well will produce or form the reheat chamber at all loads where the system requires the advantages that can be afforded by the dual pressure deaeration system herein disclosed, all of which is thought to be shown at FIGS. 2, 4 and 5 of the drawings.

The vent condenser chamber 30 will be in continuous communication. with the reheat chamber or space 42 through a plurality of passages or openings 43 in the central or chamber floor portion 36. Thus, during operation all the gas containing condensate in the condensate pan 31 which passes through the fluid seal portions 32a and 32b to the vent condenser chamber 30 will in turn pass through passages 43 to the reheat chamber or space 42 In FIGS. 4 and 5, it is further shown that there are a plurality of longitudinally extending transversely disposed fluid trays in the reheat chamber 42. The trays comprise a stack of five alternately staggered layers. The five layers of trays comprise a top layer of trays 45 having an H-shaped cross-sectional configuration and four layers therebelow of trays 47 having a gull-shaped configuration. As is evident from FIG. 5, the upper and lower edges of H-shaped trays 45 are provided with serrations. These serrations control the flow of condensate out of the trough portion of the trays to define a plurality of rivulets flowing through the V-base of the serrations and further accommodates for improved dispersion characteristics of fluid showering on the trays below by reason of the tendency of the fluid running down the side of the trays to break away from the tray surface at the pointed bottom portion of the serrations. Thus, the provision of such tray serrations insures the occurrence of a plurality of shower streams from the first layer of trays to the second layer of trays and improves the efficiency of flashing of non-condensible gases from the showering condensate.

Fluid initially enters the tray stack through a plurality of openings 43 formed in the chamber floor portion 30 of chamber 43. Thus, condensate from the collecting trough portions 32a and 32b of condensate pan 31 passes through fluid trap portions 34a and 34b and into chamber 42. It then passes through openings 43 as a shower onto I-I-shaped trays 45 whereafter the condensate showers from tray to tray until it showers off the bottom layer of trays and into the hot well 22. Each stage of showering reduces the gaseous content of the condensate. The degasified condensate is pumped out of hot well 22 for reuse, e. g. as boilerfeed water.

As may be best seen in FIG. 2, the level of condensate in hot well 22 is above the lowermost portion of the fluid trap seal portions 34a and 34b of condensate pan 31. As a result, that portion between the side walls 350 and 35d which forms the reheat chamber is pressure-isolated from the major volume of the hot well 22 of the condenser and, as is discussed below in detail, does not experience variations in pressure in response to variations of pressure in the main volume of the condenser. Thus, chamber floor portion 35 of chamber 30, trap seal portions 34a and-34b of condensate pan 31 and the surface of the condensate in hot well 22 cooperate to define the reheat chamber 42 in the hot well in which trays 45 and 47 of the tray stack are received. a H

Disposed within hot well reheat chamber 42, below the tray stack and above the surface of condensate in the reheat chamber is a longitudinally extending steam pipe 50. Pipe 50 is provided with a plurality of openings spaced along its length whereby steam introduced therethrough is caused to spray out into the reheat chamber 42.

The negative pressure generated in vent condenser chamber 30 by ejector 41 causes the steam to flow upwardly through the tray stack thereby establishing a counterflow of steam through the showering condensate. This counterflow of steam reheats any subcooled condensate and maintains an environment conducive to the separation of non-condensible gases by positive displacement based on the differential pressure maintained in the vent condenser chamber 30.

Any steam not condensed by contact with the showering condensate passes upwardly through the tray stack, through openings 43 into the vent condenser chamber 30. From vent condenser chamber 30 the steam passes to the vent condenser section 27 where any residual steam is condensed and the non-condensible gases are passed out of the condenserby operation ofthe ejector 41.

As will be recognized by those skilled in the art, the introduction of a reheating steam at the downstream section of the tray stack provides for a highly efficient reduction in the gaseous content of the condensate because it provides for a true counter-flow of reheating steam'through the showering condensate. More specifically, by providing such a counter-flow the cleanest steam is exposed to the condensate having the least gaseous content thereby providing for deaeration of the condensate in the most efficient manner. This mode of deaeration, i.e. pure counter-flow, provides for greatly improved results over known approaches which involve either parallel flow of steam and condensate or a flow of steam which is substantially normal to the direction of flow of condensate.

Considering the operation of the deaerating surface condenser above described, a flow of cooling water from a suitable source is established through tube bundles 26a and 26b and vent condenser section 27 from inlet header 17 to discharge header 18 Ejector 41 is actuated to draw the desired constant vacuum on the vent condenser chamber 30 as at all times independent, and lower than the vacuum pressure being maintained in condenser she'll during operating 15.

Exhaust steam from turbine 14 is introduced through inlet 12 and the steam dome 16 into the condenser shell 15 of condenser 10. The major portion of the exhaust steam passes through the tube bundles 26a and 26b to be condensed, although a small portion of theexhaust steam by-pass the tube bundles 26a and 26b passing through the space formed about the tube bundles 26a and 26b between the tube bundles and the sides of the condenser shell 15. This by-pass steam is utilized to provide a reheating effect on the gas-containing condensate which rains from the tube surfaces of tube bundles 26a and 26b onto the collecting trough portions 32a and 32b of condensate pan 31. The gas-containing condensate collected in trough portions 32a and 32b is thereafter passed'through fluid trap seal portions 34a and 34b to the vent condenser chamber 30. a

As noted above, vent condenser chamber 30 is under a predetermined negative pressure lower than that in the remaining portions of the interior of condenser 10 because itis in direct communication with the ejector 41. Gas-containing condensate entering vent condenser chamber 30 passes through openings 43 in the chamber floor portion 35 and in the reheat chamber 42 showers over trays 45 and 47 of the deaerating tray stack as discussed above. The condensate, which is now of a greatly reduced gas concentration, collects in hot well 22 and is removed through outlet opening 24 to be used, e.g. as boilder feed water- I FIGURE 6 FORM OF THE INVENTION In FIG. 6an alternate embodiment of the invention is illustrated which is appropriate for use with turbines furnishing steam. at two different exhaust pressures.

In this form of the invention how to be described the same parts will be given the same numbers as applied to like parts in the form of the invention shown in FIGS. 1 to 5 above described. I I

Thus, in the form of the invention in order to accommodate and separate the flow of steam by reason of the difference in pressure the condenser shell 15 and the turbine 15 are provided with a dividing wall 61 transversely of the longitudinal line of the condenser shell 15 and medially thereof as steam volume conditions require for the particular discharging pressures to form an upstream condensing chamber 62 and a downstream condensing chamber 63. i I

Division plate or wall 61 thus is in sealing engagement with the turbine 14 and the walls of inlet opening 12, steam dome 16 and the condenser shell 15 of the condenser. It extends downwardly into the condenser shell only a portion of the vertical dimension thereof short of the hot well 22. The dividing wall or plate 61 is joined to the hood 29 and condensate plate 31 to foreshorten all of the elements of or associated with the entire vent condenser section now shown and generally designated 64 in FIG. 6 of the drawings. Due to this foreshortening, tubes 28 of the vent condenser which extend from the cooling water inlet header 1? to the cooling water outlet header 18 are now partly in the vent condenser section 64 and partly in the downstream chamber 63. The portion of the tubes in the vent condenser section 64 operate in the same manner and for the same purpose as above described for the form of the invention shown in FIGS. 1 to 5 of the drawings.

The downstream condensing chamber 63 will communicate directly with the hot well 22.

The operation of the vent condensing section 61 and the parts therein is identical with the counter-flow deaearating venting section of the form of the invention shown in FIGS. 1 to 5 of the drawing.

Similarly, the respective upstream condensing chamber 62 and the downstream condensing chamber 63 will have conventional means (not shown) for maintaining the desired back pressure on the respective turbine exhaust flow so that the pressure in the downstream condensing section 63'will be at all times greater than the pressure in the upstream condensing section 62.

In operation exhausting steam from the turbine is formed into two flows, one part passing to the upstream condensing chamber 62 which is the chamber closest to the cooling water inlet header l7 and the other part will pass to the downstream condensing chamber 62 which is more remote from the cooling water inlet header 17.

All condensed fluid from the downstream condensing chamber 63 will pass into the hot well 22 directly and non-condensed steam and non-condensible gases will be passed out of the downstream condensing chamber 63 by the conventional evacuating means for setting the pressure therein.

The condensation of steam in the upstream condensing chamber 62 and the deaeration thereof through the vent condenser section 64 is identical with that above described for the form of the invention shown in FIGS. 1 to of the drawings. The vent condenser section 64 will be maintained by the ejector 41 at a pressure less than the pressure in upstream condensing chamber 62 so that positive counter-flow will be maintained in the reheat chamber 42 of the vent condenser section.

The greater pressure in the downstream condensing section will help to move fluid in the hot well 22 so as to form the reheat chamber 42 as above described.

FIGURE 7 FORM OF THE INVENTION In FIG. 7 a further embodiment of the invention is shown for turbines exhausting steam at different pres- In this form of the invention the same parts will again bear the same numbers as was used to describe the form of the invention shown in FIGS. 1 to 5 of the drawings.

Thus, we again find in this form of the invention the dividing plate or wall 71 to accommodate and separate the separate flow of steam into the upstream condensing chamber 72 adjacent the inlet cooling water header l7 and the downstream condensing chamber 73 remote from the cooling water inlet,

Division plate or wall 71 also seals off the vent condenser section generally designated 74 and the condensate pan 31 in the manner shown in FIG. 7 to again foreshorten all the elements of or associated with the vent condenser section 64 except the tubes 28 which extend from the inlet header 17 to the outlet header 18. That portion of the tubes which remains in the vent condenser section 74 will function as above described in FIGS. 1 to 5 of the drawings for the vent condenser 27.

This form of the invention, however, differs in that an imperforate transverse plate 75 is also provided in the downstream condensing chamber 73 which plate seals chamber 73 from the hot well 22 of the condenser.

The transverse plate 75 is disposed at a slightly higher level than the central or chamber floor portion 35 of the condensate plate 31 and there is formed at the point where the condensate pan 31 and the transverse plate 75 connect to the dividing plate or wall 71 a U- shaped fluid trap 76.

.8 By reference to FIG. 7 the U-shaped trap 76 includes a spaced wall members 77 and 78 and an opening 79 which is at the lower most section of the fluid passage 80 formed by the U-shaped trap 76.

5 Thus, in this form of the invention the downstream condensing chamber 73 does not communicate directly with the hot well 22. Condensate formed in the downstream condensing chamber 73 must be passed through the U-shaped fluid trap 76 to join, flow with and consequently be deaerated in the same manner as the condensate formed in the upstream condensate chamber 72.

Since the vent condenser section 74 except for the l 5 foreshortening operates identical to the vent condenser section above described for the form of the invention shown in FIGS. 1 to 5 of the drawings, it is believed that the operation of this form of the invention will be easily understood.

However, before describing the operation it will be noted once again that the upstream condensing chamber 72 and the downstream condensing chamber 73 will have conventional means (not shown) for maintaining the desired vacuum pressure on the respective 2S turbine exhaust flows so that the pressure in the downstream condensing section 73 will be at all times greater than the pressure in the vent condenser chamber 30. It is thought obvious that such differential pressure is required to effect transfer of fluid through the U-shaped fluid trap 76.

In operation exhausting steam from the turbine is formed into two flows, one part passing to the upstream condensing chamber 72 and the other part passing to the downstream condensing chamber 73.

All condensate from the downstream condensing chamber 73 will pass through the U-shaped fluid trap to join condensate from the upstream condensing chamber 72 which collects and passes through the fluid trap portions 34a and 34b to the central or chamber floor portion 35 of the vent condenser chamber 30.

Thereafter the operation of the counter-flow deaeration of the condensate through the vent condenser section 74 will be the same as was described for the form 4 5 of the invention shown in FIGS. 1 to 5 of the drawings.

These deaerating condensers according to the invention are considered to be a significant improvement over those known in the art because the structure is simple and provides for efflcient reduction in the content of non-condensible gases in condensate notwithstanding variations in the load conditions placed on the condenser. In this regard, it has been found that oxygen concentrations of 0.005 cubic centimeter of oxygen per liter of condensate has been maintained over virtually all conditions of loading in condensers struc- 9 exchange means disposed in the shell for condensing vapor in said condensing chamber to form a condensate having non-condensable gases entrained therein, a hot well for deaerated condensate having an outlet for withdrawing said deaerated condensate from said shell, and means connected to said shell for maintaining a negative pressure in said condensing chamber,

c. means disposed in the shell intermediate the condensing chamber and the hot well for collecting said gas containing condensate,

d. means on said collecting means forming fluid seal means,

e. means in saidshell for deaerating said gas containing condensate, I

f. said deaerating means including means operatively associated with said fluid seal means to form a vent chamber in continuous communication withthe deaerating means and disposed to receive said gas containing condensate from said collecting means through said fluid trap means,

g. means for maintaining said deaerating means and chamber means at a constant predetermined pressure independent of and less than the lowest environmental pressure in said condensing chamber when said apparatus is in operation,

h. means on said collecting means operatively associated with said hot well to form a reheat space therein and for passing deaerated condensate to said hot well,

. said chamber means disposed relative the collecting means and having passage means for passing said gas containing condensate to said reheat space,

j. and means in said reheat space to provide a flow of heating vapor counter to the flow of the gas con- I taining condensate entering said reheat space from thepassage means in said chamber means.

2. 2. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 1 wherein,

a. the means for collecting said gas containing condensate includes, a transversely disposed member connected in said shell below the heat exchange means and above the hot well,

b. and spaced depending portions on the transverse member disposed during operation to extend into the deaerated condensate in the hot well to form said reheat space.

3. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 2 wherein:

a. the deaerating means includes, casing means having spaced sides walls disposed to extend into the spaced depending portions of the transverse member to form said fluid seal means and to define said vent chamber with the transverse member.

4. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 2 wherein:

a. the passage means for the vent chamber is disposed in the transverse member,

b. means in the reheat space including spaced trays 6 c. and the means for establahing a flow of heated vapor in the reheat space consists of pipe means having openings. thereon connected to a clean source of said heated vapor and disposed in said reheat space below the spaced trays.

5. In the apparatus for condensing and deaerating a vapor containing non-condensible gas as claimed in claim 2 including,

a. division means in said shell to divide said condensing chamber into a first condensing space having a first inlet for receiving vapor at a first pressure to be condensed ,ancl a second condensing space having a second inlet for vapor at a second pressure t be condensed, I

said means for maintaining a negative pressure in said condensing chamber connected to maintain the respective first condensing space" and the second condensing psace at pressures adapted to cause said vapor to be condensed to flow into said a first condensing space and said second condensing space respectively.

c. and said deaerating means is disposed in said condensing spaces. I n

6. In the apparatus for condensing and deaerating a vapor containing non-condensiblegas as claimed in claim 5 further including,

a means to pass gas containing condensate from said second condensing space to the chamber in said deaerating means.

7. In combination,

a. steam turbine means having at least one discharge outlet for steam, and

b. apparatus for condensing and deaerating said steam including,

1. a shell forming a condensing chamber,

2. said shell having an inlet for passing steam to be condensed into said condensing chamber, heat exchange means disposed in the shell for condensing steam in said condensing chamber to form a condensate having non-condensible gases entrained therein, a hot well for deaerated condensate having an outlet for withdrawing said deaerated condensate from said shell, and means connected to said shell for maintaining a negative pressure in said condesnsing chamber,

c. means disposed in the shell intermediate the condensing chamber and the hot well for collecting said gas containing d. means on said collecting means forming fluid seal means,

e. means in said shell for deaerating said gas containing condensate,

. said deaerating means including means operatively associated with said fluid seal means to form a vent chamber in continuous communication with the deaerating means and disposed to receive said gas containing condensate from said collecting means through siad fluid trap means,

g. means for maintaining said deaerating means and chamber means at a constant predetermined pressure independent of and less than the lowest environmental pressure in said condensing chamber when said apparatus is in operation,

h. means on said collecting means operativly as sociated with said hot well to form a reheat space therein and for passing deaerated condensate to said hot well,

i. said chamber means disposed relative the 'collecitng means and having passage means for passing said gas containing condensate to said reheat space, v v

j. and means in said reheat space to provide a flow of heating vapor counter to the flow of the gas containing condensate entering said reheat space from the passage means in said chamber means,

8. The combination as claimed in claim 7 wherein the steam turbine has plural exhaust outlets for steam,

and r a. means in the shell to divide the condensing chamber into a first condensing space and a second condensing space for accommodating flow of exhaust steam from the outlet of chamber, steam turbine at two distinct pressure levels into said condensing chamber, I

b. the means for maintaining said condensing chamber at a negative pressure connected to maintain a lower negative pressure in said first condensing space than the negative pressure in said second condensing space,

0. said means for deaerating gas containing condensate disposed in said first condensing space,

(1. and said dividing means bounding said first condensing chamber whereby condensate formed in said second condensing chamber passes directly into said hot well.

9. The combination as claimed in claim 7 wherein the steam turbine has plural exhaust outlets for steam,

and

a. means in the shell to divide the condensing chamber into a first condensing space and a second condensing space for accomodating flow of exhaust steam from the outlet of said steam turbine at two distinct pressure levels, into said condensing chamber,

b. the means for maintaining said condensing chamber at a negative pressure connected to maintain a lower pressure in said first condensing space than the negative pressure in said second condensing space,

c. said means for deaerating gas containing condensate disposed in said first condensing space,

d. said division plate disposed transversely in said shell, I

. an inperforate plate mounted in the shell intermediate the second condensing space and the hot well and normal to the line of the division plate,

f. a fluid trap seal in communication at one end with the second condensing space to receive gas containing condensate therefrom and at the other end communicates with the lower negative pressure first condensing space whereby gas containing condensate from the second condensing space will flow through said fluid trap seal to the first condensing space,

. and passage means to pass fluid from the fluid trap seal to the vent chamber in said deaerating means. 

1. Apparatus for condensing and deaerating a vapor containing non-condensable gases comprising: a. a shell forming the condensing chamber, b. said shell having an inlet for passing vapor to be condensed into saiD condensing chamber, heat exchange means disposed in the shell for condensing vapor in said condensing chamber to form a condensate having non-condensable gases entrained therein, a hot well for deaerated condensate having an outlet for withdrawing said deaerated condensate from said shell, and means connected to said shell for maintaining a negative pressure in said condensing chamber, c. means disposed in the shell intermediate the condensing chamber and the hot well for collecting said gas containing condensate, d. means on said collecting means forming fluid seal means, e. means in said shell for deaerating said gas containing condensate, f. said deaerating means including means operatively associated with said fluid seal means to form a vent chamber in continuous communication with the deaerating means and disposed to receive said gas containing condensate from said collecting means through said fluid trap means, g. means for maintaining said deaerating means and chamber means at a constant predetermined pressure independent of and less than the lowest environmental pressure in said condensing chamber when said apparatus is in operation, h. means on said collecting means operatively associated with said hot well to form a reheat space therein and for passing deaerated condensate to said hot well, i. said chamber means disposed relative the collecting means and having passage means for passing said gas containing condensate to said reheat space, j. and means in said reheat space to provide a flow of heating vapor counter to the flow of the gas containing condensate entering said reheat space from the passage means in said chamber means.
 2. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 1 wherein, a. the means for collecting said gas containing condensate includes, a transversely disposed member connected in said shell below the heat exchange means and above the hot well, b. and spaced depending portions on the transverse member disposed during operation to extend into the deaerated condensate in the hot well to form said reheat space.
 2. said shell having an inlet for passing steam to be condensed into said condensing chamber, heat exchange means disposed in the shell for condensing steam in said condensing chamber to form a condensate having non-condensible gases entrained therein, a hot well for deaerated condensate having an outlet for withdrawing said deaerated condensate from said shell, and means connected to said shell for maintaining a negative pressure in said condesnsing chamber, c. means disposed in the shell intermediate the condensing chamber and the hot well for collecting said gas containing condensate, d. means on said collecting means forming fluid seal means, e. means in said shell for deaerating said gas containing condensate, f. said deaerating means including means operatively associated with said fluid seal means to form a vent chamber in continuous communication with the deaerating means and disposed to receive said gas containing condensate from said collecting means through siad fluid trap means, g. means for maintaining said deaerating means and chamber means at a constant predetermined pressure independent of and less than the lowest environmental pressure in said condensing chamber when said apparatus is in operation, h. means on said collecting means operativly associated with said hot well to form a reheat space therein and for passing deaerated condensate to said hot well, i. said chamber means disposed relative the collecitng means and having passage means for passing said gas containing condensate to said reheat space, j. and means in said reheat space to provide a flow of heating vapor counter to the flow of the gas containing condensate entering said reheat space from the passage means in said chamber means,
 3. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 2 wherein: a. the deaerating means includes, casing means having spaced sides walls disposed to extend into the spaced depending portions of the transverse member to form said fluid seal means and to define said vent chamber with the transverse member.
 4. In the apparatus for condensing and deaerating a vapor containing non-condensible gases as claimed in claim 2 wherein: a. the passage means for the vent chamber is disposed in the transverse member, b. means in the reheat space including spaced trays to increase the counter flow contact between the gas containing condenstte and the heated vapor supplied in the reheat space, c. and the means for establahing a flow of heated vapor in the reheat space consists of pipe means having openings thereon connected to a clean source of said heated vapor and disposed in said reheat space below the spaced trays.
 5. In the apparatus for condensing and deaerating a vapor containing non-condensible gas as claimed in claim 2 including, a. division means in said shell to divide said condensing chamber into a first condensing space having a first inlet for receiving vapor at a first pressure to be condensed and a second condensing space having a second inlet for vapor at a second pressure to be condensed, said means for maintaining a negative pressure in said condensing chamber connected to maintain the respective first condensing space and the second condensing psace at pressures adapted to cause said vapor to be condensed to flow into said first condensing space and said second condensing space respectively. c. and said deaerating means is disposed in said condensing spaces.
 6. In the apparatus for condensing and deaerating a vapor containing noN-condensible gas as claimed in claim 5 further including, a means to pass gas containing condensate from said second condensing space to the chamber in said deaerating means.
 7. In combination, a. steam turbine means having at least one discharge outlet for steam, and b. apparatus for condensing and deaerating said steam including,
 8. The combination as claimed in claim 7 wherein the steam turbine has plural exhaust outlets for steam, and a. means in the shell to divide the condensing chamber into a first condensing space and a second condensing space for accommodating flow of exhaust steam from the outlet of chamber, steam turbine at two distinct pressure levels into said condensing chamber, b. the means for maintaining said condensing chamber at a negative pressure connected to maintain a lower negative pressure in said first condensing space than the negative pressure in said second condensing space, c. said means for deaerating gas containing condensate disposed in said first condensing space, d. and said dividing means bounding said first condensing chamber whereby condensate formed in said second condensing chamber passes directly into said hot well.
 9. The combination as claimed in claim 7 wherein the steam turbine has plural exhaust outlets for steam, and a. means in the shell to divide the condensing chamber into a first condensing space and a second condensing space for accomodating flow of exhaust steam from the outlet of said steam turbine at two distinct pressure levels, into said condensing chamber, b. the means for maintaining said condensing chamber at a negative pressure connected to maintain a lower pressure in said first condensing space than the negative pressure in said second condensing space, c. said means for deaerating gas containing condensate disposed in said first condensing space, d. said division plate disposed transversely in said shell, e. an inperforate plate mounted in the shell intermediate the second condensing space and the hot well and normal to the line of the division plate, f. a fluid trap seal in communication at one end with the second condensing space to rEceive gas containing condensate therefrom and at the other end communicates with the lower negative pressure first condensing space whereby gas containing condensate from the second condensing space will flow through said fluid trap seal to the first condensing space, g. and passage means to pass fluid from the fluid trap seal to the vent chamber in said deaerating means. 